US20210239384A1 - Refrigerator - Google Patents
Refrigerator Download PDFInfo
- Publication number
- US20210239384A1 US20210239384A1 US17/168,354 US202117168354A US2021239384A1 US 20210239384 A1 US20210239384 A1 US 20210239384A1 US 202117168354 A US202117168354 A US 202117168354A US 2021239384 A1 US2021239384 A1 US 2021239384A1
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- US
- United States
- Prior art keywords
- pipe
- working fluid
- evaporator
- fluid
- opening
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 239000012530 fluid Substances 0.000 claims abstract description 262
- 238000003860 storage Methods 0.000 claims abstract description 117
- 238000005086 pumping Methods 0.000 claims abstract description 110
- 239000003507 refrigerant Substances 0.000 claims abstract description 29
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 26
- 239000000463 material Substances 0.000 claims description 11
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 claims description 10
- 230000008602 contraction Effects 0.000 claims description 6
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 claims description 5
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 claims description 5
- 229910052782 aluminium Inorganic materials 0.000 claims description 5
- 229910052802 copper Inorganic materials 0.000 claims description 5
- 239000010949 copper Substances 0.000 claims description 5
- 229910052742 iron Inorganic materials 0.000 claims description 5
- 238000010257 thawing Methods 0.000 description 34
- 239000003570 air Substances 0.000 description 24
- 239000012071 phase Substances 0.000 description 18
- 239000007791 liquid phase Substances 0.000 description 10
- 238000001816 cooling Methods 0.000 description 8
- CSCPPACGZOOCGX-UHFFFAOYSA-N Acetone Chemical compound CC(C)=O CSCPPACGZOOCGX-UHFFFAOYSA-N 0.000 description 7
- 230000008018 melting Effects 0.000 description 5
- 238000002844 melting Methods 0.000 description 5
- 239000004020 conductor Substances 0.000 description 4
- 238000007710 freezing Methods 0.000 description 4
- 230000008014 freezing Effects 0.000 description 4
- LFQSCWFLJHTTHZ-UHFFFAOYSA-N Ethanol Chemical compound CCO LFQSCWFLJHTTHZ-UHFFFAOYSA-N 0.000 description 3
- OKKJLVBELUTLKV-UHFFFAOYSA-N Methanol Chemical compound OC OKKJLVBELUTLKV-UHFFFAOYSA-N 0.000 description 3
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 2
- 238000009835 boiling Methods 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- -1 for example Substances 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 230000003252 repetitive effect Effects 0.000 description 2
- 239000005060 rubber Substances 0.000 description 2
- 229910052710 silicon Inorganic materials 0.000 description 2
- 239000010703 silicon Substances 0.000 description 2
- 229910001220 stainless steel Inorganic materials 0.000 description 2
- 239000010935 stainless steel Substances 0.000 description 2
- 229920003002 synthetic resin Polymers 0.000 description 2
- 239000000057 synthetic resin Substances 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 238000009834 vaporization Methods 0.000 description 2
- 230000008016 vaporization Effects 0.000 description 2
- 239000012080 ambient air Substances 0.000 description 1
- 229910021529 ammonia Inorganic materials 0.000 description 1
- 238000004590 computer program Methods 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 230000006870 function Effects 0.000 description 1
- 230000014759 maintenance of location Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
- F25D21/06—Removing frost
- F25D21/12—Removing frost by hot-fluid circulating system separate from the refrigerant system
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
- F25D21/002—Defroster control
- F25D21/006—Defroster control with electronic control circuits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
- F25D21/06—Removing frost
- F25D21/08—Removing frost by electric heating
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
- F25D21/14—Collecting or removing condensed and defrost water; Drip trays
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
- F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
- F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
- F28F1/325—Fins with openings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
- F28F19/006—Preventing deposits of ice
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
- F25D11/02—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D2321/00—Details or arrangements for defrosting; Preventing frosting; Removing condensed or defrost water, not provided for in other groups of this subclass
- F25D2321/14—Collecting condense or defrost water; Removing condense or defrost water
- F25D2321/146—Collecting condense or defrost water; Removing condense or defrost water characterised by the pipes or pipe connections
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
- F28D2021/0071—Evaporators
Definitions
- the pumping part may be configured to move the vaporized working fluid along a circulation channel far away from the fluid storage.
- FIG. 9 illustrates an expansion state of the pumping part in FIG. 8 ;
- FIG. 19 illustrates a configuration of a defroster according to an eighth embodiment of the disclosure.
- the refrigerator 1 may be not limited by many various structures or uses, but embodied by all the kinds of refrigerators having the refrigerator compartment or the freezer compartment.
- the ice-making compartment 13 may be provided with an ice-making unit 131 for making ice, and an ice-storage container 132 for storing ice made by the ice-making unit 131 .
- the ice stored in the ice-storage container 132 may be discharged through a duct 133 .
- the cooling system 20 may include a compressor 21 , a condenser 22 , a switching valve 23 , a first expansion valve 24 , a second expansion valve 25 , the evaporators 26 and 27 , and a refrigerant pipe 28 .
- the switching valve 23 selectively supplies the liquefied refrigerant from the condenser 22 to the ice-making compartment 13 or the evaporator of the freezer compartment 11 .
- the control program may include a program(s) achieved by at least one of a basic input/output system (BIOS), a device driver, an operating system (OS), a firmware, a platform, or an application.
- BIOS basic input/output system
- OS operating system
- the application may be previously installed or stored in the refrigerator 1 when the refrigerator 1 is manufactured, or may be installed in the refrigerator 1 on the basis of application data received from the outside when it is required in the future.
- the application data may for example be downloaded from an external server such as an application market to the refrigerator 1 .
- Such an external server is merely an example of the computer program product, but not limited thereto.
- the evaporator 26 may include a refrigerant pipe 262 through which the refrigerant is transferred, and a plurality of heat-exchanging fins 264 installed to be in contact with the refrigerant pipe 262 .
- the refrigerant pipe 262 is extended in two parallel rows when viewed from the side.
- the piping 34 may be extended from the first opening 324 of the fluid storage 32 along the refrigerant pipe 262 of the evaporator 26 via the pumping part 36 and connected to the second opening 326 of the fluid storage 32 .
- the processor 50 applies power to the heater 364 of the pumping part 36 when the defrosting operation starts.
- the defroster 30 shown in FIG. 16 includes the first and second pipings 34 - 1 and 34 - 2 having the first and second circulation channels with respect to the fluid storage 32 and the pumping part 36 , respectively, but may alternatively include three or more pipings.
- the refrigerator according to the disclosure employs a heat-pumping type defroster to thereby defrost the evaporator at a higher efficiency than heat transfer of a conventional heater based on radiation and convection.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Geometry (AREA)
- Defrosting Systems (AREA)
Abstract
Description
- This application is based on and claims priority under 35 U.S.C. § 119 to Korean Patent Application No. 10-2020-0013422 filed on Feb. 5, 2020 in the Korean Intellectual Property Office, the disclosure of which is incorporated by reference herein in its entirety.
- The disclosure relates to a refrigerator, and more particularly to a defroster that removes frost covering an evaporator of a refrigerator.
- An original function of a refrigerator is to keep food fresh for long. To this end, the refrigerator employs a cooling system including a compressor, a condenser, an evaporator, etc. to lower the temperature of a freezer compartment or a refrigerator compartment as desired. In this case, air introduced into the freezer compartment or the refrigerator compartment exchanges heat with the evaporator and becomes cold air. Further, moisture in air is attached to the surface of the evaporator. Then, frost continuously accumulated on the surface of the evaporator and decreases a heat-exchange efficiency. To maintain heat-exchange performance, a conventional refrigerator performs defrosting by regularly operating a heater placed below the evaporator. In this case, defrosting water from melting frost drains into a defrosting water tray through a drain hose connected to a lower drain plate.
- The frost formed on the evaporator is melted by radiant and convection energy from the surface of the heater installed below. However, a considerable amount of input energy causes temperature to increase in the evaporator, the shelf and the inside of the refrigerator, and thus lowers an energy efficiency because temperature needs to be decreased as much as the increased temperature when the refrigerator operates.
- An aspect of the disclosure is to provide a refrigerator in which frost covering an evaporator is efficiently removed.
- According to an embodiment of the disclosure, there is provided a refrigerator with a storage space. The refrigerator includes an evaporator configured to cool air in the storage space based on heat exchange of a refrigerant, and a defroster configured to remove frost formed on the evaporator. The defroster includes a piping configured to go via the evaporator and including a circulation channel through which working fluid circulates, a fluid storage including a first opening and a second opening respectively communicating with opposite end portions of the piping and configured to store the circulating working fluid, a pumping part provided at a certain position on the circulation channel of the piping between the evaporator and the fluid storage and configured to vaporize the working fluid to circulate the working fluid in the circulation channel.
- The first opening may be positioned lower than the second opening, and the pumping part may be provided at a certain position on the circulation channel between the first opening of the first storage and the evaporator.
- The piping may be provided at an upper position than the fluid storage.
- The first opening may be provided lower than a level of the working fluid, and the second opening may be provided higher than the level of the working fluid.
- The pumping part may include a thermal conductive block including a fluid passage through which the working fluid passes, and a heater provided in the thermal conductive block and configured to generate heat.
- The thermal conductive block may include at least one of aluminum, copper or iron.
- The defroster further may include a drain plate provided below the evaporator and configured to collect defrosting water from melting frost.
- At least one of the thermal conductive block or the fluid storage may be provided to be in contact with the drain plate.
- The pumping part may include a pipe connector configured to connect the piping to the fluid passage of the thermal conductive block.
- The pipe connector may include a lower thermal-conductivity material than the piping.
- The pipe connector may include a material of low thermal conductivity, and the piping may include a material of high thermal conductivity.
- The piping may include a first piping, the circulation channel may include a first circulation channel, and the defroster may further include at least one second piping with a second circulation channel returned from the fluid storage via the pumping part and the evaporator.
- The pumping part may include a thermal conductive block including a first fluid passage through which the working fluid of the first piping passes, and a second fluid passage through which the working fluid of the second piping passes.
- The piping may include a first piping configured to go via a first area of the evaporator, and a second piping configured to go via a second area of the evaporator, the fluid storage may include a first fluid storage provided on a circulation channel between a first end portion of the first piping and a first end portion of the second piping, the pumping part may include a first pumping part provided on a circulation channel between the first area and the first opening of the first fluid storage, and the defroster may include a second fluid storage provided on a circulation channel between a second end portion of the first piping and a second end portion of the second piping, and configured to store the working fluid, and a second pumping part provided on the circulation channel of the second piping part between the second fluid storage and the second area.
- The fluid storage may include a first fluid storage configured to store a first working fluid, the piping may include a first piping configured to go via a first area of the evaporator, the pumping part may include a first pumping part provided on a first circulation channel between a first area of the evaporator and the first fluid storage, and the defroster may include a second piping configured to go via a second area of the evaporator, and including a second circulation channel in which a second working fluid circulates, a second fluid storage including a third opening and a fourth opening respectively communicating with opposite end portions of the second piping, and configured to store second working fluid, and a second pumping part provided at a certain position on the second circulation channel of the second piping between the second area of the evaporator and the second fluid storage, and configured to vaporize the second working fluid to circulate the second working fluid in the second circulation channel.
- The first pumping part may include a first thermal conductive block with a first fluid passage through which working fluid of the first piping passes, the second pumping part may include a second thermal conductive block with a second fluid passage through which working fluid of the second piping passes, and the defroster may include a heater interposed between the first thermal conductive block and the second thermal conductive block.
- The piping may include a first piping, the pumping part may include a first pumping part, the fluid storage may further include a third opening and a fourth opening, and the defroster may include a second piping configured to go via the evaporator, and including opposite end portions respectively communicating with the third opening and the fourth opening of the fluid storage, and a second circulation channel in which the working fluid flows between the opposite end portions, and a second pumping part provided at a certain position on the second circulation channel of the second piping between the evaporator and the fluid storage, and configured to vaporize the working fluid to circulate the working fluid in the second circulation channel.
- The pumping part may be configured to move the vaporized working fluid along a circulation channel far away from the fluid storage.
- The pumping part may be configured to be closer to the first opening than the second opening.
- The pumping part may be configured to pump the working fluid based on expansion and contraction of the working fluid.
- The above and/or the aspects will become apparent and more readily appreciated from the following description of exemplary embodiments, taken in conjunction with the accompanying drawings, in which:
-
FIG. 1 is a perspective view of a refrigerator according to a first embodiment of the disclosure; -
FIG. 2 is a lateral cross-section view schematically showing the refrigerator according to the first embodiment of the disclosure; -
FIG. 3 is a block diagram of the refrigerator according to the first embodiment of the disclosure; -
FIG. 4 illustrates a defroster installed in an evaporator according to the first embodiment of the disclosure; -
FIG. 5 is a lateral view of the defroster installed in the evaporator according to the first embodiment of the disclosure; -
FIG. 6 illustrates a piping installed in an evaporator according to an embodiment of the disclosure; -
FIG. 7 illustrates a piping installed in an evaporator according to another embodiment of the disclosure; -
FIG. 8 illustrates a structure of a pumping part; -
FIG. 9 illustrates an expansion state of the pumping part inFIG. 8 ; -
FIG. 10 illustrates a contraction state of the pumping part inFIG. 8 ; -
FIG. 11 illustrates a schematic configuration of the defroster according to the first embodiment of the disclosure; -
FIG. 12 is a flowchart showing a defrosting operation according to the first embodiment of the disclosure; -
FIG. 13 is a perspective view showing a pumping part according to a second embodiment of the disclosure; -
FIG. 14 illustrates a defroster installed in an evaporator according to a third embodiment of the disclosure; -
FIG. 15 illustrates a defroster installed in an evaporator according to a fourth embodiment of the disclosure; -
FIG. 16 illustrates a configuration of a defroster according to a fifth embodiment of the disclosure; -
FIG. 17 illustrates a configuration of a defroster according to a sixth embodiment of the disclosure; -
FIG. 18 illustrates a configuration of a defroster according to a seventh embodiment of the disclosure; -
FIG. 19 illustrates a configuration of a defroster according to an eighth embodiment of the disclosure; and -
FIG. 20 illustrates a configuration of a defroster according to a ninth embodiment of the disclosure. - Below, embodiments of the disclosure will be described in detail with reference to the accompanying drawings so as to be easily realized by a person having ordinary knowledge in the art to which the disclosure pertains. The disclosure may be embodied in various different forms, but not limited to the embodiments set forth herein.
-
FIG. 1 is a perspective view of a refrigerator according to a first embodiment of the disclosure. - The
refrigerator 1 according to the first embodiment of the disclosure may for example be embodied by a general-type, double-door type, or three- to four-door type refrigerator according to the number of doors and methods of opening the door. - Further, the
refrigerator 1 according to the disclosure may for example be embodied by a 1-EVA, 2-EVA, or 3-EVA type refrigerator according to the number of evaporators for supplying cool air. - Further, the
refrigerator 1 according to the first embodiment of the disclosure may include a refrigerator having a refrigerator compartment and a freezer compartment where ice is made, a freezer having a freezer compartment for making ice, or an ice maker only for making ice. - Further, the
refrigerator 1 according to the first embodiment of the disclosure may include an indirect-cooling type or direct-cooling type standing refrigerator or a built-in premium freezer. - As described above, the
refrigerator 1 according to the disclosure may be not limited by many various structures or uses, but embodied by all the kinds of refrigerators having the refrigerator compartment or the freezer compartment. -
FIG. 2 is a lateral cross-section view schematically showing therefrigerator 1 according to the first embodiment of the disclosure; - Referring to
FIG. 2 , therefrigerator 1 may include amain body 10 which includes afreezer compartment 11, arefrigerator compartment 12 and an ice-makingcompartment 13, and acooling system 20 which supplies cold air to thefreezer compartment 11, therefrigerator compartment 12 and the ice-makingcompartment 13. - The
main body 10 may include afreezer compartment door 14 for opening/closing thefreezer compartment 11, and arefrigerator compartment door 15 for opening/closing therefrigerator compartment 12. - A user may open the
freezer compartment door 14 to store things in thefreezer compartment 11. Thefreezer compartment 11 may be provided with a freezingbox 16, and a user may keep things frozen in the freezingbox 16. - The
freezer compartment 11 may be provided with a first cold-air supplying duct 17 on a rear wall. The first cold-air supplying duct 17 may be provided with a freezer-compartment evaporator 27 of thecooling system 20, and afreezer fan 17 a, and a freezer-compartment cold-air outlet 17 b. Thefreezer fan 17 a may be configured to supply cold air, with which heat is exchanged by the freezer-compartment evaporator 27, to thefreezer compartment 11 through the freezer-compartment cold-air outlet 17 b. - A user may open the
refrigerator compartment door 15 to store things in therefrigerator compartment 12. Therefrigerator compartment 12 may be provided with a plurality ofshelves 18, and a user may put things on theselves 18 and keep the things refrigerated. - The
refrigerator compartment 12 may be provided with a second cold-air supplying duct 19 on the rear wall. The second cold-air supplying duct 19 may be provided with a refrigerator-compartment evaporator 26 of thecooling system 20, and arefrigerator fan 19 a. A refrigerator-compartment cold-air outlet 19 b may be provided between the second cold-air supplying duct 19 and therefrigerator compartment 12. Therefrigerator fan 19 a may be configured to supply cold air, with which heat is exchanged by the refrigerator-compartment evaporator 26, to therefrigerator compartment 12 through the refrigerator-compartment cold-air outlet 19 b. - The ice-making
compartment 13 is partitioned from therefrigerator compartment 12 by an ice-making compartment casing forming a predetermined space therein, and insulated from therefrigerator compartment 12. - The ice-making
compartment 13 may be provided with an ice-makingunit 131 for making ice, and an ice-storage container 132 for storing ice made by the ice-makingunit 131. The ice stored in the ice-storage container 132 may be discharged through aduct 133. - The
cooling system 20 may include acompressor 21, acondenser 22, a switchingvalve 23, afirst expansion valve 24, asecond expansion valve 25, theevaporators refrigerant pipe 28. Below, only theevaporator 26 of thefreezer compartment 11 will be representatively described because theevaporator 26 of thefreezer compartment 11 is structurally analogous to theevaporator 27 of therefrigerator compartment 12. - The
compressor 21 compresses a refrigerant into gas of high temperature and high pressure. Specifically, thecompressor 21 may include a motor to compress the refrigerant. - The
condenser 22 condenses the gaseous refrigerant of high temperature and high pressure supplied from thecompressor 21 into liquid by heat exchange with external air. - The switching
valve 23 selectively supplies the liquefied refrigerant from thecondenser 22 to the ice-makingcompartment 13 or the evaporator of thefreezer compartment 11. - The
first expansion valve 24 makes the refrigerant of low temperature and high pressure to be supplied to the ice-makingcompartment 13 pass through a capillary tube and thus have low pressure. - The
second expansion valve 25 makes the refrigerant of low temperature and high pressure to be supplied to theevaporator 26 pass through a capillary tube and thus have low pressure. - The
evaporator 26 makes the refrigerant of low temperature and low pressure coming through thesecond expansion valve 25 perform heat exchange with air of thefreezer compartment 11 and therefrigerator compartment 12. Based on the cooling cycle of the refrigerant, theevaporator 26 evaporates the refrigerant while the liquefied refrigerant of low temperature low pressure moves along a refrigerant pipe of theevaporator 26. Further, theevaporator 26 makes the refrigerant absorb heat, which is necessary for evaporation, from ambient air. Thus, cold air cooled by theevaporator 26 may be formed around theevaporator 26. In this case, relative humidity is lowered as air is cooled around theevaporator 26, thereby causing condensation that water vapor contained in air passing through theevaporator 26 is condensed. Further, water of which temperature is below its freezing point is frozen and formed as frost on the surface of theevaporator 26. Alternatively, water vapor in air may be sublimated into frost by colliding with the surface of theevaporator 26 having low temperature. - The refrigerant flowing in the
refrigerant pipe 28 is discharged from thecompressor 21 and supplied to theevaporator 26 provided in the refrigerator compartment and the freezer compartment via thecondenser 22 and thesecond expansion valve 25. -
FIG. 3 is a block diagram of therefrigerator 1 according to the first embodiment of the disclosure. - Referring to
FIG. 3 , therefrigerator 1 may include thecompressor 21, theevaporator 26, adefroster 30, atemperature sensor 40, and aprocessor 50. Here, thecompressor 21 and theevaporator 26 were described above with reference toFIG. 2 , and thus repetitive descriptions thereof will be avoided. - The
defroster 30 can remove frost from theevaporator 26. Specifically, thedefroster 30 may generate heat and melt frost covering theevaporator 26. The structure and operations of thedefroster 30 will be described later. - The
temperature sensor 40 detects temperature around theevaporator 26. Specifically, thetemperature sensor 40 may be placed at one side of theevaporator 26 and detect temperature to identify phase transition of the frost covering theevaporator 26. Here, thetemperature sensor 40 may be placed at a position spaced apart from thedefroster 30 to make sure whether the front covering theevaporator 26 is completely removed. - The
processor 50 controls the elements of therefrigerator 1. Specifically, theprocessor 50 may control thedefroster 30 for a defrosting operation to defrost theevaporator 26. - The
processor 50 may identify whether a defrosting signal for carrying out the defrosting operation of thedefroster 30 is input. The defrosting signal may be a signal detected by thetemperature sensor 40. - Alternatively, the
processor 50 may generate the defrosting signal when input information satisfies a certain condition. For example, theprocessor 50 may generate the defrosting signal when accumulated time in a timer for measuring an operating time of thecompressor 21 reaches a preset time. - Alternatively, the
processor 50 may generate the defrosting signal based on a value sensed by a sensor using light for detecting an accumulated amount of frost covering theevaporator 26 or a sensor for detecting electric capacity between heat-exchanging fins of theevaporator 26. - The
processor 50 may control thedefroster 30 until a preset condition for completing the defrosting operation is satisfied, for example, until a defrosting time or a temperature sensed at theevaporator 26 reaches a predetermined threshold. - The
processor 50 includes at least one general-purpose processor that loads at least a part of a control program from a nonvolatile memory installed with the control program to a volatile memory and executes the loaded control program, and may for example be embodied by a central processing unit (CPU), an application processor (AP), or a microprocessor. - The
processor 50 may include a single-core processor, a dual-core processor, a triple-core processor, a quad-core processor, or the like multiple-core processor. Theprocessor 50 may include a plurality of processors. Theprocessor 50 may for example include a main processor and a sub processor that operates in a sleep mode (e.g. a mode where only standby power is supplied). Further, the processor, the read only memory (ROM), and the random access memory (RAM) may be connected to one another through an internal bus. - The
processor 50 may be embodied as included in a main system on chip (SoC) to be mounted to a printed circuit board (PCB) internally provided in therefrigerator 1. - The control program may include a program(s) achieved by at least one of a basic input/output system (BIOS), a device driver, an operating system (OS), a firmware, a platform, or an application. The application may be previously installed or stored in the
refrigerator 1 when therefrigerator 1 is manufactured, or may be installed in therefrigerator 1 on the basis of application data received from the outside when it is required in the future. The application data may for example be downloaded from an external server such as an application market to therefrigerator 1. Such an external server is merely an example of the computer program product, but not limited thereto. -
FIG. 4 illustrates thedefroster 30 installed in theevaporator 26 according to the first embodiment of the disclosure,FIG. 5 is a lateral view of thedefroster 30 installed in theevaporator 36 according to the first embodiment of the disclosure,FIG. 6 illustrates a piping 34 installed in anevaporator 26 according to an embodiment of the disclosure,FIG. 7 illustrates a piping 34 installed in anevaporator 26 according to another embodiment of the disclosure, andFIG. 8 illustrates a structure of a pumpingpart 36. - Referring to
FIGS. 4 and 5 , theevaporator 26 may include arefrigerant pipe 262 through which the refrigerant is transferred, and a plurality of heat-exchangingfins 264 installed to be in contact with therefrigerant pipe 262. Referring toFIG. 5 , therefrigerant pipe 262 is extended in two parallel rows when viewed from the side. - The
defroster 30 may include afluid storage 32 in which working fluid is stored, a piping 34 in which the working fluid flows, a pumpingpart 36, and adrain plate 38. - The
fluid storage 32 may be filled with the working fluid at a certain level. The working fluid may for example include water, freon refrigerant, ammonia, acetone, methanol, ethanol, or a mixture thereof. For example, the working fluid may include acetone which has a freezing point of −94° C. not to be frozen at the lowest temperature of therefrigerator 1, e.g. about −30° C. and a boiling point of 56° C. higher than a room temperature. - The
fluid storage 32 may include afirst opening 324 through which the working fluid goes out, and asecond opening 326 through which the working fluid comes in. Thefirst opening 324 may be positioned lower than thesecond opening 326. Thefirst opening 324 may be positioned lower than the level of the working fluid, and thesecond opening 326 may be positioned higher than the level of the working fluid. - The
fluid storage 32 may be placed below theevaporator 26. - The
fluid storage 32 may be provided to be in contact with the bottom of thedrain plate 38. Specifically, thefluid storage 32 may be installed on a first mountingportion 382 protruding horizontally from an inclined bottom of thedrain plate 38. Thefluid storage 32 may store the working fluid in a liquid phase of e.g. about 30-40° C. as the working fluid in a gas phase heated e.g. at 56° C. in the pumpingpart 36 exchanges heat with the frost on theevaporator 26. In result, thefluid storage 32 maintains a temperature for example at 30-40° C. while the pumpingpart 36 is continuously operating. Therefore, ice in thedrain plate 38 may be melted by heat transferred by thefluid storage 32. Of course, the temperature of the working fluid in the liquid phase come back to and stored in thefluid storage 32 may be varied depending on a degree of exchanging heat between the heated work fluid in the gas phase and theevaporator 26, for example, depending on the length or diameter of the piping 34, and the ambient temperature of theevaporator 26. That is, the working fluid in the liquid phase may have a temperature lower than 30° C. when there is much frost or the ambient temperature of theevaporator 26 is low, and may have a temperature higher than 40° C. when there is less frost or the temperature of theevaporator 26 is high. When the pumpingpart 36 does not operate, the temperature of the working fluid in thefluid storage 32 may be decreased up to the temperature of the space where theevaporator 26 is installed, for example, up to −30° C. - The piping 34 may have ends respectively communicating with the
first opening 324 and thesecond opening 326 of thefluid storage 32. The piping 34 may include a circulation channel in which the working fluid flows between both ends thereof. - The piping 34 may be extended from the
first opening 324 of thefluid storage 32 along therefrigerant pipe 262 of theevaporator 26 via the pumpingpart 36 and connected to thesecond opening 326 of thefluid storage 32. - The piping 34 may include a
first pipe 341 connecting the pumpingpart 36 and thefirst opening 324 of thefluid storage 32, and asecond pipe 342 connecting the pumping part and thesecond opening 326 of thefluid storage 32. - The piping 34 may be extended from the
fluid storage 32 and the pumpingpart 36 toward theevaporator 26 positioned higher than thefluid storage 32 and the pumpingpart 36. - The piping 34 may be more densely arrayed in a lower portion of the
evaporator 26 because frost the lower portion of theevaporator 26 is more frosted than an upper portion thereof. For instance, the piping 34 may pass for example twice through the heat-exchangingfins 264 of thelower refrigerant pipe 262, but pass once through the heat-exchangingfins 264 of theupper refrigerant pipe 262. - Alternatively, the piping 34 passing through the heat-exchanging
fins 264 of thelower refrigerant pipe 262 of theevaporator 26 may have a larger diameter than the piping 34 passing through the heat-exchangingfins 264 of the upper portion, thereby enlarging a contact area for heat exchange. - Referring to
FIG. 6 , the piping 34 may be installed to be in contact with the heat-exchangingfins 264 of theevaporator 26. The piping 34 may be fitted to openedgrooves 2642 of the heat-exchangingfins 264. - Referring to
FIG. 7 , the piping 34 may be fitted toclosed holes 2643 of the heat-exchangingfins 264. - The pumping
part 36 may be provided at a certain position in the circulation channel of the piping 34, and vaporize the working fluid, thereby circulating the working fluid in the circulation channel. - The pumping
part 36 may be installed below theevaporator 26. - The pumping
part 36 may be installed on the circulation channel of the piping 34 closer to thefirst opening 324 than thesecond opening 326 of thefluid storage 32. - Referring to
FIG. 8 , the pumpingpart 36 may include a thermalconductive block 362, aheater 364, and first and second pipe connectors 366-1 and 366-2. - The thermal
conductive block 362 may include afluid passage 3622 through the working fluid passes. The working fluid passing through the thermalconductive block 362 may be vaporized by heat generated in theheater 364. - The thermal
conductive block 362 may be shaped like a hexahedron or a cylinder. - The thermal
conductive block 362 may include a highly thermal conductive material, for example, at least one of aluminum, copper or iron. - The thermal
conductive block 362 may be installed to be in contact with the bottom of thedrain plate 38 as shown inFIG. 4 . Specifically, the thermalconductive block 362 may be installed on a second mountingportion 384 horizontally protruding from the inclined bottom of thedrain plate 38. Thus, when the thermalconductive block 362 is heated by theheater 364, thedrain plate 38 being in contact with the thermalconductive block 362 may also be heated. In result, ice remaining in thedrain plate 38 may be melted by heat transferred from the thermalconductive block 362. - The
heater 364 may generate heat when powered on. Theheater 364 may be installed being in contact with one surface of the thermalconductive block 362. Theheater 364 may operate by theprocessor 50 according to preset conditions. Specifically, theprocessor 50 may operate the heater when the temperature of theevaporator 26 sensed by thetemperature sensor 40 provided in theevaporator 26 reaches a threshold value. - The
heater 364 may be embodied by a positive temperature coefficient (PTC) heater. - The first pipe connector 366-1 may connect with the
first pipe 341 for connection between the thermalconductive block 362 and thefirst opening 324 of thefluid storage 32. The first pipe connector 366-1 may include a material having lower thermal conductivity than the material of thefirst pipe 341, for example, silicon, rubber, synthetic resin, etc. In this case, thefirst pipe 341 may include a highly thermal conductive material, for example, copper, aluminum, iron, stainless steel, etc. The first pipe connector 366-1 having such low thermal conductivity interrupts heat transfer from the thermalconductive block 362 heated by theheater 364 toward thefirst pipe 341, thereby causing the working fluid in the gas phase moved to thefirst pipe 341 to smoothly contract. - The second pipe connector 366-2 may connect with the
second pipe 342 for connection between the thermalconductive block 362 and thesecond opening 326 of thefluid storage 32. The second pipe connector 366-2 may include a material having lower thermal conductivity than the material of thesecond pipe 342, for example, silicon, rubber, synthetic resin, etc. In this case, thesecond pipe 342 may include a highly thermal conductive material, for example, copper, aluminum, iron, stainless steel, etc. The second pipe connector 366-2 having such low thermal conductivity interrupts heat transfer from the thermalconductive block 362 heated by theheater 364 toward thesecond pipe 342, thereby causing the working fluid in the gas phase moved to thesecond pipe 342 to smoothly contract. - The foregoing pumping
part 36 includes the thermalconductive block 362 and theheater 364, but is not limited to this. The pumpingpart 36 may include any structure as long as it can vaporize the working fluid in thepipe 34. For example, the pumpingpart 36 may be embodied by a hot wire provided to surround thepipe 34. - Referring back to
FIGS. 4 and 5 , thedrain plate 38 may be placed covering the bottom of theevaporator 26, and collect pieces of ice or defrosting water or from melting the frost on theevaporator 26. - The
drain plate 38 may include the first mountingportion 382 on which thefluid storage 32 is installed, the second mountingportion 384 on which thepumping part 36 is installed, and adefrosting water outlet 386 through which the defrosting water is discharged. The first mountingportion 382 and the second mountingportion 384 may for example be formed to horizontally protrude at a predetermined height from a partial bottom of thedrain plate 38 by press work. The defrosting water discharged through thedefrosting water outlet 386 may be collected in a water tank through a hose. - The ice collected in the
drain plate 38 may be melted by heat from thefluid storage 32 and/or the pumpingpart 36. -
FIG. 9 illustrates an expansion state of the pumpingpart 36 inFIG. 8 , andFIG. 10 illustrates a contraction state of the pumpingpart 36 inFIG. 8 . - Referring to
FIG. 9 , when theheater 364 operates, the working fluid in the liquid phase filled in the thermalconductive block 362 may be vaporized. In this case, the working fluid in the gas phase moves from the thermalconductive block 362 to both thefirst pipe 341 and thesecond pipe 342 as its volume is expanded. In this case, the working fluid in the gas phase expanded to the opposite sides farther moves toward thesecond pipe 342 empty or filled with the working fluid in the gas phase rather than thefirst pipe 341 filled with the working fluid in the liquid phase. - Referring to
FIG. 10 , the working fluid in the gas phase expanded toward both thefirst pipe 341 and thesecond pipe 342 may be contracted by heat exchange with an ambient atmosphere of thefirst pipe 341 and thesecond pipe 342, for example, cold air in a space where theevaporator 26 is placed and frost formed in the heat-exchangingfins 364 of theevaporator 26. In this case, the amount of working fluid in the gas phase moved to thesecond pipe 342 is more than that of the working fluid in the gas phase moved to thefirst pipe 341, and therefore the pressure at thesecond pipe 342 may become lower than that at thefirst pipe 341. With such difference in pressure, the working fluid in the liquid phase of thefluid storage 32 moves toward thesecond pipe 342 and is thus filled in the thermalconductive block 362. - When the expansion and contraction of the working fluid shown in
FIGS. 9 and 10 are repeated, the pumpingpart 36 pumps the vaporized working fluid toward thesecond pipe 342 passing through the area of theevaporator 26 while repeating vaporization and suction of the working fluid. - Below, an operation principle of the
defroster 30 will be described in detail. -
FIG. 11 illustrates a schematic configuration of thedefroster 30 according to the first embodiment of the disclosure, andFIG. 12 is a flowchart showing a defrosting operation according to the first embodiment of the disclosure. - At operation S11, the
processor 50 applies power to theheater 364 of the pumpingpart 36 when the defrosting operation starts. - At operation S12, heat generated by the
heater 364 is transferred to the thermalconductive block 362. - At operation S13, when the thermal
conductive block 362 is heated up to the boiling point, e.g. 56° C. of the working fluid, e.g. acetone, the working fluid of the piping 34 passing through the thermalconductive block 362 may be vaporized by the phase transition from liquid to gas. - At operation S14, the working fluid in the gas phase may be expanded toward both the
first pipe 341 and thesecond pipe 342 of the thermalconductive block 362 by difference in density as shown inFIG. 9 . - At operation S15, the working fluid in the gas phase expanded toward the
first pipe 341 and thesecond pipe 342 may be contracted by dissipating heat toward the outside while the heat transfer is interrupted by the first and second pipe connectors 366-1 and 366-2 made of the low thermal conductive material. - At operation S16, the working fluid in the gas phase moved to the first and second pipe connectors 366-1 and 366-2 is contracted, and thus the working fluid in the liquid phase in the
fluid storage 32 moves toward thesecond pipe 342 having lower pressure as shown inFIG. 10 and fills the thermalconductive block 362. - At operation S17, the vaporization, expansion, contraction and suction pumping shown in the operations S13 to S16 are repetitively performed.
- The pumped working fluid in the gas phase is moved to the piping 34 in the area of the
evaporator 26 and transfers heat to frost on theevaporator 36, thereby melting the frost. - At operation S18, the
processor 50 checks a preset condition for completing the defrosting operation, for example, the defrosting time or the temperature of the heat-exchangingfins 264 of theevaporator 36. When the condition for completing the defrosting operation is not satisfied, theheater 364 is continuously powered on. - At operation S19, when the condition for completing the defrosting operation is satisfied, the
heater 364 is powered off. - As described above, the
defroster 30 according to the first embodiment of the disclosure pushes out the working fluid in the gas phase of high temperature toward the frost covering theevaporator 26 so that the working fluid can move to thesecond opening 326 of thefluid storage 32 after heat transfer, and pulls in the working fluid in the liquid phase of thefluid storage 32 toward the pumpingpart 36 through thefirst opening 324, thereby pumping the working fluid. - The
defroster 30 according to the first embodiment of the disclosure performs one-way circulation pumping in which thepumping part 36 is fed with the working fluid in the liquid phase, the working fluid in the gas phase is pumped toward theevaporator 26 and contracted in theevaporator 26, and the working fluid in the liquid phase is returned to thefluid storage 32, thereby efficiently pumping the working fluid and thus improving a defrosting efficiency. - Further, the
fluid storage 32 and the pumpingpart 36 are installed being in contact with thedrain plate 38, thereby melting ice in thedrain plate 38 at the defrosting operation. -
FIG. 13 is a perspective view showing a pumpingpart 66 according to a second embodiment of the disclosure. - Referring to
FIG. 13 , the pumpingpart 66 may include a thermalconductive block 662, and aheater 664. - In the pumping
part 66 according to the second embodiment, unlike the pumpingpart 36 according to the first embodiment shown inFIG. 8 , thefirst pipe 341 and thesecond pipe 342 may be directly connected to the thermalconductive block 662 without the first and second pipe connectors 366-1 and 366-2. - Alternatively, one of the
first pipe 341 and thesecond pipe 342 may be directly connected to the thermalconductive block 662, but the other one may be connected via the pipe connector. -
FIG. 14 illustrates adefroster 30 installed in anevaporator 26 according to a third embodiment of the disclosure. - Referring to
FIG. 14 , thedefroster 30 may include afluid storage 62 in which working fluid is stored, a piping 34 in which the working fluid flows, a pumpingpart 36, and adrain plate 68. - The
fluid storage 62 may include an inclinedsecond bottom portion 628 being in contact with an inclinedfirst bottom portion 681 of thedrain plate 68. In result, thefluid storage 62 is vertically mounted onto the inclinedfirst bottom portion 681 of thedrain plate 68 without inclination. - The
first pipe 341 of the piping 34 may be extended to be in parallel with the inclinedfirst bottom portion 681 of thedrain plate 68. - The pumping
part 36 may be mounted onto the inclinedfirst bottom portion 681 of thedrain plate 68 as inclined. - Thus, the
drain plate 68 of thedefroster 30 according to the third embodiment excludes the first mountingportion 382 for the installation of thefluid storage 32 and the second mountingportion 384 for the installation of the pumpingpart 36, unlike thedrain plate 38 shown inFIG. 4 . -
FIG. 15 illustrates adefroster 30 installed in anevaporator 26 according to a fourth embodiment of the disclosure. - Referring to
FIG. 15 , thedefroster 30 may include afluid storage 72 in which working fluid is stored, a piping 34 in which the working fluid flows, a pumpingpart 36, and adrain plate 78. - The
fluid storage 72 may be mounted onto an inclinedfirst bottom portion 781 of thedrain plate 78 as inclined. - Likewise, the pumping
part 36 may be mounted onto the inclinedfirst bottom portion 781 of thedrain plate 78 as inclined. -
FIG. 16 illustrates a configuration of adefroster 30 according to a fifth embodiment of the disclosure. Below, the descriptions of the same or similar configurations according to the first embodiment shown inFIG. 11 will be omitted. - Referring to
FIG. 16 , thedefroster 30 may include a first piping 34-1 and a second piping 34-2 in which working fluid flows. - The
fluid storage 32 may include afirst opening 324 and athird opening 325 through which working fluid goes out, and asecond opening 326 and afourth opening 327 through which the working fluid comes in. - The first piping 34-1 may include opposite ends respectively communicating with the
first opening 324 of thefluid storage 32 and thesecond opening 326 positioned higher than thefirst opening 324. The first piping 34-1 may include a first circulation channel in which the working fluid flows between both ends thereof. - The first piping 34-1 may be extended from the
first opening 324 of thefluid storage 32 along therefrigerant pipe 262 of theevaporator 26 via the pumpingpart 36 and connected to thesecond opening 326 of thefluid storage 32. - The second piping 34-2 may include opposite ends respectively communicating with the
third opening 325 of thefluid storage 32 and thefourth opening 327 positioned higher than thethird opening 325. The second piping 34-2 may include a second circulation channel in which the working fluid flows between both ends thereof. - The second piping 34-2 may be extended from the
third opening 325 of thefluid storage 32 along therefrigerant pipe 262 of theevaporator 26 via the pumpingpart 36 and connected to thefourth opening 327 of thefluid storage 32. - The pumping
part 36 may be provided at a certain position in the first and second circulation channels of the first and second pipings 34-1 and 34-2, and vaporize the working fluid, thereby circulating the working fluid in the first and second circulation channels. - The thermal
conductive block 362 may include afirst fluid passage 3622 through which the first piping 34-1 passes, and asecond fluid passage 3624 through which the second piping 34-2 passes. The thermalconductive block 362 may use heat generated by theheater 364 to vaporize the working fluid flowing in the first and second pipings 34-1 and 34-2 passing therethrough. - The
defroster 30 shown inFIG. 16 includes the first and second pipings 34-1 and 34-2 having the first and second circulation channels with respect to thefluid storage 32 and the pumpingpart 36, respectively, but may alternatively include three or more pipings. - As described above, the
defroster 30 according to the fifth embodiment circulates the working fluid through the plurality of circulation channels, so that the whole channel length can be shortened or the pipings 34-1 and 34-2 can be more densely arranged in theevaporator 26, thereby improving a defrosting efficiency. -
FIG. 17 illustrates a configuration of adefroster 30 according to a sixth embodiment of the disclosure. - Referring to
FIG. 17 , thedefroster 30 may include first and second fluid storages 32-1 and 32-2 in which working fluid is stored, first and second pipings 34-1 and 34-2 in which the working fluid flows, and the first and second pumping parts 36-1 and 36-2. - The first fluid storage 32-1 may be filled with the working fluid at a certain level. The first fluid storage 32-1 may include a
first opening 324 through which the working fluid goes out, and asecond opening 326 through which the working fluid comes in. Thefirst opening 324 may be positioned lower than thesecond opening 326. Thefirst opening 324 may be positioned lower than the level of the working fluid, and thesecond opening 326 may be positioned higher than the level of the working fluid. - The second fluid storage 32-2 may be filled with the working fluid at a certain level. The second fluid storage 32-2 may include a
fifth opening 328 through which the working fluid goes out, and asixth opening 329 through which the working fluid comes in. Thefifth opening 328 may be positioned lower than thesixth opening 329. Thefifth opening 328 may be positioned lower than the level of the working fluid, and thesixth opening 329 may be positioned higher than the level of the working fluid. - The first piping 34-1 may form a first circulation channel connecting the
first opening 324 of the first fluid storage 32-1, the first pumping part 36-1, and thesixth opening 329 of the second fluid storage 32-2. In this case, the first circulation channel between the first pumping part 36-1 and the second fluid storage 32-2 may go via a first area 26-1 of theevaporator 26 to thereby remove frost. - The second piping 34-2 may form a second circulation channel connecting the
fifth opening 328 of the second fluid storage 32-2, the second pumping part 36-2, and thesecond opening 326 of the first fluid storage 32-1. The second circulation channel between the second pumping part 36-2 and the first fluid storage 32-1 may go via a second area 26-2 of theevaporator 26 to thereby remove frost. -
FIG. 17 illustrates that the first fluid storage 32-1 and the first pumping part 36-1 are arranged below theevaporator 26, and the second fluid storage 32-2 and the second pumping part 36-2 are arranged above theevaporator 26, but the arrangement is not limited this illustration. For example, all the first fluid storage 32-1, the first pumping part 36-1, the second fluid storage 32-2, and the second pumping part 36-2 may be arranged above or below theevaporator 26. - The
defroster 30 shown inFIG. 17 includes a first defrosting group including the first piping 34-1, the first fluid storage 32-1 and the first pumping part 36-1 to form the first circulation channel, and a second defrosting group including the second piping 34-2, the second fluid storage 32-2, and the second pumping part 36-2 to form the second circulation channel, but may alternatively include three or more defrosting groups. - As described above, the
defroster 30 according to the sixth embodiment includes the plurality of defrosting groups in series on one wholly-connected circulation channel, thereby finishing the defrosting operation in a short period of time. -
FIG. 18 illustrates a configuration of adefroster 30 according to a seventh embodiment of the disclosure. - Referring to
FIG. 18 , thedefroster 30 may include a first defroster 30-1 which includes a first fluid storage 32-1 in which first working fluid is stored, a first piping 34-1 in which the first working fluid flows, and a first pumping part 36-1, and a second defroster 30-2 which includes a second fluid storage 32-2 in which second working fluid is stored, a second piping 34-2 in which second working fluid flows, and a second pumping part 36-2. - The first defroster 30-1 and the second defroster 30-2 may include circulation channels independently of each other, and respectively defrost the first area 26-1 and the second area 26-2 of the
evaporator 26. Of course, the first defroster 30-1 and the second defroster 30-2 may remove frost from the first area 26-1 and the second area 26-2 in cooperation with each other. - Each of the first defroster 30-1 and the second defroster 30-2 has the same configurations and operations as the
defroster 30 according to the first embodiment shown inFIG. 11 , and thus repetitive descriptions thereof will be omitted. - The
defroster 30 shown inFIG. 18 includes the first defroster 30-1 and the second defroster 30-2 which are independent of each other, but may alternatively include three or more defrosters which are independent of one another. - As described above, the
defroster 30 according to the seventh embodiment includes the plurality of independent defrosters arranged in theevaporator 26 to thereby divisionally defrost theevaporator 26. For example, the frost may be focused in a lower portion of theevaporator 26, and thus the lower defrosters among the upper and lower independent defrosters may operate for a longer period of time or more frequently. -
FIG. 19 illustrates a configuration of adefroster 30 according to an eighth embodiment of the disclosure. - Referring to
FIG. 19 , thedefroster 30 may include afluid storage 32 in which working fluid is stored, first and second pipings 34-1 and 34-2 in which the working fluid flows, and first and second pumping parts 36-1 and 36-2. - While the
defroster 30 according to the second embodiment shown inFIG. 16 employs thesingle pumping part 36 to heat the working fluid in the first piping 34-1 and the second piping 34-2, thedefroster 30 according to the eighth embodiment shown inFIG. 19 employs the first pumping part 36-1 and the second pumping part 36-2 to heat the working fluid in the first piping 34-1 and the second piping 34-2. - The
defroster 30 according to the eighth embodiment includes the first and second pumping parts 36-1 and 36-2 respectively arranged in two pipings 34-1 and 34-2, but alternatively include three or more pumping parts respectively arranged in three or more pipings. - As described above, the
defroster 30 according to the eighth embodiment sufficiently provides heat in a short period of time while the working fluid circulates in the plurality of pipes, thereby improving a defrosting efficiency. -
FIG. 20 illustrates a configuration of adefroster 30 according to a ninth embodiment of the disclosure. - Referring to
FIG. 20 , thedefroster 30 may include afluid storage 32 in which working fluid is stored, first and second pipings 34-1 and 34-2 in which the working fluid flows, and apumping part 36. - In the
defroster 30 according to the ninth embodiment, the pumpingpart 36 may include a first thermal conductive block 362-1, a second thermal conductive block 362-2, and aheater 364. In this case, theheater 364 may be interposed between the first thermal conductive block 362-1 and the second thermal conductive block 362-2. - Like this, the
heater 364 is placed in between the first thermal conductive 362-1 and the second thermal conductive 362-2, thereby minimizing an outward heat release thereof. - As described above, the refrigerator according to the disclosure employs a heat-pumping type defroster to thereby defrost the evaporator at a higher efficiency than heat transfer of a conventional heater based on radiation and convection.
- Although a few embodiments of the disclosure have been described in detail, various changes can be made in the disclosure without departing from the scope of claims.
Claims (20)
Applications Claiming Priority (2)
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KR1020200013422A KR20210099719A (en) | 2020-02-05 | 2020-02-05 | Refrigerator |
KR10-2020-0013422 | 2020-02-05 |
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US20210239384A1 true US20210239384A1 (en) | 2021-08-05 |
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US17/168,354 Pending US20210239384A1 (en) | 2020-02-05 | 2021-02-05 | Refrigerator |
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US (1) | US20210239384A1 (en) |
KR (1) | KR20210099719A (en) |
WO (1) | WO2021157994A1 (en) |
Cited By (1)
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CN114322421A (en) * | 2021-12-31 | 2022-04-12 | 长虹美菱股份有限公司 | Refrigerator defrosting device and control method |
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JP2012122652A (en) * | 2010-12-07 | 2012-06-28 | Mitsubishi Electric Corp | Refrigerator |
KR101437938B1 (en) * | 2008-07-11 | 2014-09-05 | 한라비스테온공조 주식회사 | Air conditioning system for automotive vehicles |
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KR19980023161A (en) * | 1996-09-25 | 1998-07-06 | 배순훈 | Cooler Defrost System of Refrigerator |
KR100431348B1 (en) * | 2002-03-20 | 2004-05-12 | 삼성전자주식회사 | refrigerator |
KR100494389B1 (en) * | 2002-08-06 | 2005-06-13 | 삼성전자주식회사 | Refrigerator and defroster |
KR101125827B1 (en) * | 2010-05-03 | 2012-03-27 | 김종수 | Defrosting module with loop-type heat pipe using bubble jet |
CN206504506U (en) * | 2017-01-18 | 2017-09-19 | 合肥美的电冰箱有限公司 | Plate pipe evaporator and refrigerator |
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2020
- 2020-02-05 KR KR1020200013422A patent/KR20210099719A/en unknown
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2021
- 2021-02-02 WO PCT/KR2021/001352 patent/WO2021157994A1/en active Application Filing
- 2021-02-05 US US17/168,354 patent/US20210239384A1/en active Pending
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KR101437938B1 (en) * | 2008-07-11 | 2014-09-05 | 한라비스테온공조 주식회사 | Air conditioning system for automotive vehicles |
CN201772430U (en) * | 2010-08-10 | 2011-03-23 | 鸿茂电器国际有限公司 | Steam generating device |
JP2012122652A (en) * | 2010-12-07 | 2012-06-28 | Mitsubishi Electric Corp | Refrigerator |
US20170131018A1 (en) * | 2015-11-11 | 2017-05-11 | Lg Electronics Inc. | Defrosting device and refrigerator having the same |
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CN114322421A (en) * | 2021-12-31 | 2022-04-12 | 长虹美菱股份有限公司 | Refrigerator defrosting device and control method |
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WO2021157994A1 (en) | 2021-08-12 |
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